Rotary disc disintegrator



B. J. PARMELE ROTARY DISC DISI NTEGRATOR May 9,1967

3 Sheets-Sheet 1 Filed 001:. 28, 1964 E n? T M NR m WJ ATTORNEY May 9, 1967 B. J. PARMELE 3,317,975

I ROTARY DISC DISINTEGRATOR Filed Oct. 28, 1964 3 Sheets-Sheet 2 FIG. 2

INVENTOR. BENJAMIN J. PARMELE BY [I 0 A TTOR EEY May 9, 1967 Filed Oct, 28, 1964 FIG. 4

IIIIlIII/IIIIII A B. J. PARMELE ROTARY DISC DISINTEGRATOR 5 Sheets-Sheet 5 o 86 30L IIIIIl'IIIIIII/IIIIIJ o 80 7 amok? 94 amo IIIII IIIIIIIIIIIII, u 890 FIG. 5

INVENTOR, BENJAMIN J. PARMELE ATTORNEY.

United States Patent 3,317,975 ROTARY DISC DISINTEGRATOR Benjamin J. Parmele, 1601 /2 Princess St., Wilmington, N.C. 28401 Filed Oct. 28, 1964, Ser. No. 407,067 8 Claims. (Cl. 241-484) water slurry, and are piped away from it to the next stage of fiber preparation.

In the aforesaid Paul patent, there are a pair of opposed discs rotating in opposite directions about a common horizontal axis, the discs having annular flanges on their faces which interdigitate with one another. The shaft supporting one of the discs is hollow, and the material is screw fed through the hollow shaft into the center of the space surrounded by the disc flanges. The discs are axially spaced from one another at a fixed distance and the annular flanges are in circular planes at right-angles to the disc surfaces.

According to this invention, it is intended to provide for the adjustment of the axial spacing between the discs, and to incline the annular flanges inwardly towards the axis of the discs, with the following results: First, when the discs are adjusted axially relative to one another, the length of the zigzag path along which the material flows from the center of the discs to the outlet through the casing which surrounds the peripheries of the discs is established to produce optimum results. Second, because of the inward inclination of the interdigitating annular flanges, axial adjustment of the discs relative to one another varies the spaces in the radial direction of the discs between the free edges of the annular flanges on one of the discs and the outer surfaces of the annular flanges on the other disc.

A further object in connection with the inward inclination of the annular flanges on the opposed discs is to provide an arrangement wherein the free edges of the annular flanges of one disc do not run in compacted material which has become pocketed along the inner surfaces of the annular flanges on the opposite disc. It has been found that the material which is thrown by the centrifugal force outwardly against the inner surfaces of the annular flanges builds up along those inner surfaces. This buildup of material varies according to the foot-per-minute speed at which the flanges travel so that there is more build-up on the inner annular flanges than on the outer, and the build-up material assumes an angle of repose such that it is somewhat thicker at the junctures of the annular flanges with the discs than it is adjacent the free edges of the discs. When, as in the prior art, the annular flanges are at right angles to the faces of the discs, as seen in cross-section taken diametrically through the discs, and where the overlap between the annular flanges on respective discs is substantial, then the free edges of the annular flanges on one disc run in material which flows along the surfaces of the retained material which has built up on the inner sides of the annular flanges on the other disc, the result being that the drag on the discs is excessive, the annular flanges wear excessively along their free edges, and it requires excessive power to drive the discs.

It is believed that the inward inclination of the annular flanges reduces the angle of repose of the material which 3,317,975 Patented May 9, 1967 pockets on the inner surfaces of the annular flanges. Accordingly, it is intended now to incline the annular flanges towards the axis of the discs more inwardly than those towards the periphery of the discs. While the angles of inclination will vary according to the radii of the annular flanges and the designed operating speeds of the discs, in the present example the innermost flange is preferably inclined at an angle of about 8430 with respect to the disc, and the outermost annular flange is preferably at about 89.

A further object in connection with the graduation of the inward inclination of the annular flanges, wherein those flanges nearer the axis are the more inwardly inclined, is to provide deeper pockets along the inner sides of the flanges for accommodating the larger chips. By the time the material reaches the radially outward annular flanges the chips or pieces of material being processed are broken up into a pulpy mass of particles and fiber, and hence relatively shallow pockets are suflicient to accommodate them. However, when the chips first enter between the discs and engage the inner ones of the annular flanges, there is a build-up along the inner surfaces of the inner flanges, and relatively deep pockets are required to accommodate them. According to the invention, the depth of the pockets on the inner sides of the annular flanges are controlled by the inward inclination of the flanges, and the corresponding peripheral velocities.

Still another object of the invention is to provide axially-extending traction cleats annularly spaced on the inner sides of the inwardly inclined annular flanges, these being particularly important where the material passing through the disintegrator is a liquid slurry.

These and other objects will be apparent from the following specification and drawings, in which:

FIG. 1 is a vertical section taken longitudinally through the disintegrator along the line 1-1 of FIG. 2;

FIG. 2 is a view of the left-hand end of the disintegrator as shown in FIG. 1;

FIG. 3 is an enlarged fragmentary section showing the lower half of the discs, baflles and traction cleats, with the discs in relative close axial relationship;

FIG. 4 is a view similar to FIG. 3, but showing the same parts in their relative positions after the discs have been axially separated from one another by retracting the movable chassis; and,

FIG. 5 is a diagrammatic view of the discs and baflles shown in FIG. 3 with the traction cleats removed, illustrating typical angles of inward inclination of the annular flanges, and the estimated angles of repose of compacted slurry on the inner sides of the flanges.

Referring now to the drawings, in which like reference numerals denote similar elements, the principal working parts of the disintegrator 2 are enclosed within a cylindrical shell 4 comprised of a pair of flat annular plates 6 and 8 having overlapping peripheral flanges 10 and 12 slidably sealed by packing 14. Plate 6 is fixedly con nected by a flange 15 to a fixed base plate 16 suitably anchored, as by hooks 18, to a foundation, such as rails 20. Peripheral flange 12 has at its bottom one or more outlets 22 for the material processed by the disintegrator.

Casing plate 8 is secured by a flange 24 to the floor 26 of a movable chassis 28, the latter being anchored in desired position by suitable means, such as hooks 30. Bearings 32, axles 34 and wheels 36 rollably support chassis 28 on rails 20 so that the chassis may be wheeled back and forth, either to expose the working parts within shell 4 for cleaning or repairs, or for relative adjustment described hereinbelow.

A lengthwise center plate 40 and transverse brace plates 42, 44 mount a split support tube 46, tube 46 consisting of upper and lower halves 46a and 461), respectively, having flanges 48, 50, 52 and 54 joined by bolts 56. Clamped within fixed support tube 46 is a hollow feed tube 58 connected to a flexible hose 60 which is held on by a conventional clamp 62. Hose 60 leads from a source of supply of the material to be disintegrated and water. Surrounding the inner end of feed tube 58 is a bearing 64 which rotatably supports a sheave 66 driven, via belt 68, by a motor 70, which also has a sheave 71 over which belt 68 engages' Motor 70 is mounted on floor 26 off to one side of chassis 28. Bolts 72 support an annular disc 74 on sheave 66 within casing 4, and on the working face of disc 74 are radially spaced concentric inwardly inclined annular flanges 76, 78, 80, 82 and 84. Annularly spaced around the inner sides of the annular flanges are secured traction lugs 86, i.e., upstanding, generally axially extending ribs. Traction lugs 86 are shown in FIGS. 3 and 4, but are removed in FIGS. 1 and for purposes of clarity.

Spaced opposite disc 74 is another disc 88 also having on the working face thereof a series of radially spaced, inwardly inclined annular flanges 92, 94, 96 and 98 which interdigitate with the annular flanges on disc 74, and on the inner surfaces of the annular flanges on disc 88 there also are traction lugs 108. The term inwardly inclined, as applied to the annular flanges, means that their free edges are closer to the common axis of the discs 7 4, 88 than their junctures with the discs. Typical angles of inward inclination of the annular flanges, and their effects, will be described hereinbelow.

Disc 88 is supported by bolts 102 on a sheave 104 which, in turn, is rotatably supported by a bearing 106 on a hollow feed tube 108. Sheave 104 is driven by a belt and motor, not shown, similar to belt and motor 68 and 70, the rotations of the motors being such that discs 74 and 88 are rotated in opposite directions. Around the outer end of tube 108 a clamp 110 holds on a supply tube 114 which also leads from the source of material to be disintegrated and water. Feed tube 108 is supported by a split support tube 116 which is supported by longitudinal and transverse support plates 118, 120 above fixed base 16. Suitable seals 121, 123 diagrammatically indicated in FIG. 1, are provided between plates 6 and 8 and feed tubes 58, 108, and between plates 6 and 8 and sheaves 66 and 184.

The results of adjusting chassis 26 to vary the axial spacing between discs 74 and 88 are seen by comparing FIGS. 3 and 4 with one another. When discs 74 and 88 are relatively close to one another, the distance between the free edge of one annular flange, for example, flange 98, and the outer side of the next innermost flange 84 is indicated as D1 (FIG. 3). When discs 74 and 88 are more widely spaced in the axial direction from one another, as illustrated in FIG. 4, the distance D2 between the free edge of annular flange 98 and the outer side of annular flange 84 is appreciably greater, and the overlap between the interdigitating annular flange is decreased. This results in less working of the material passing along its tortuous and turbulent course between the annular flanges, and reduces the drag of the material on the discs and flanges.

FIG. 5 diagrammatically illustrates typical inward inclination of the annular flanges. The innermost annular flange 84 on disc 74 is disposed at about 8430 with respect to the surface of disc '74, the inward inclination decreasing in about 1 steps in the progression of the flanges. Approximately the same 1 steps apply to annular flanges 98, 96, 94, 92 and 90, flange 98 being at about 85 with respect to the surface of disc 88, and flange being at about 89.

Some of the material flowing radially outwardly under centrifugal force compacts against the inner surfaces of the flange and assumes an angle of repose. Because of the extremely high velocities of the material, and because of the many particle sizes, the many directions in which they fly on their radially outward course, the precise movements of the particles is not known, but it is believed that they become pocketed and build up in dense or relatively compacted, wedge-shape areas somewhat as indicated in FIG. 5. The outward graduation of the angles of inclination of the annular flanges is designed to form deeper pockets for the material on the inner sides of the inner flanges than on the inner sides of the other ones. The deeper pockets are to accommodate the larger chips or particles which have not yet become shredded or disintegrated on the inner sides of the inner flanges whose peripheral speeds are the lesser, and the angle of repose of the surface zone, indicated in broken lines in FIG. 5 is such that the inner side of the densified zone of material nearly parallel with the outer surface of the next inward flange. Were the inclination of the surface of the densified or compacted zones of material on the inner sides of the flanges much steeper than as indicated in FIG. 5, then the free edges of the flanges would run in the zone of compacted material and more drag would ensue. The particular angles of inward inclination should vary according to the diameters of the discs, axial length and number of the annular flanges, and designed speed of rotation of the discs.

The invention is not limited to the details shown and described herein, but is intended to cover all substitutions, modifications and equivalents within the scope of the following claims.

I claim:

1. A disintegrating machine comprising a support, first and sec-0nd discs having opposed working faces with a plurality of interdigitating radially spaced annular flanges thereon, first means mounting the first disc on said base for rotation about an axis, second means including a trackway parallel to said axis and a chassis engaging said trackway mounting said second disc on said support for rotation about a horizontal axis aligned with the aforesaid axis, said chassis being movable on said trackway to provide variable axial spacing between the discs, at least some of said annular flanges which are adjacent to one another being inclined inwardly towards the axes of said discs whereby adjustment of the axial spacing between the discs provides adjustment of the radial spacing between the adjacent inclined annular flanges, a casing surrounding said discs, means for rotating said discs in opposite directions, means for feeding material to be disintegrated centrally between said discs, and outlet means in the periphery of said casing for the egress of material after the latter has passed between said annular flanges.

2. The combination claimed in claim 1, at least some of said annular flanges having annularly spaced traction lugs on the radially inward sides thereof.

3. The combination claimed in claim. 1, the inward inclination of the annular flanges which are disposed near the rotational axes of the discs being greater than the inward inclination of those which are disposed relatively outward therefrom.

4. A disintegrating machine comprising a base, a first support extending upwardly from said base, a first disc having a working face with a plurality of radially spaced annular flanges thereon, first shaft means and first bearing means mounting said first disc on said first support for rotation about a horizontal axis, a movable chassis mounted on said base, a second support extending upwardly from said chassis, a second disc having a working face opposed to the working face of the first disc and having a pluarility of radially spaced annular flanges thereon, second shaft means and second bearing means mounting said second disc on said second support for rotation about a horizontal axis aligned with the firstnamed horizontal axis, the flanges on the discs extending towards and interdigitating with one another, a hollow cylindrical casing surrounding and enclosing said discs, means for rotating said discs in opposite directions, at least one of said shaft means being hollow for supplying material to be disintegrated centrally between the discs, and outlet means through the periphery of said casing,

said chassis being movable on said base towards and away from said first support, whereby the spacing between said discs may be adjusted.

5. The combination claimed in claim 4, said casing comprising two separable parts each including a discshape end wall afiixed to a respective one of said supports and a peripheral portion, the peripheral portions of the casing parts telescopically engaging one another, whereby said casing parts may contract and expand towards and away from one another during adjustment of said discs towards and away from one another.

6. The combination claimed in claim 4, said annular flanges each having a plurality of axially-extending circumferentially spaced ribs thereon.

7. The combination claimed in claim 4, the annular flanges on said discs being inclined inwardly towards the axis of rotation of the discs whereby adjustment of the discs towards and away from one another varies the spacing between the free edges of the flanges on one disc and the radially outward sides of the flanges on the other disc.

8. The combination claimed in claim 7, the inward inclination of the annular flanges which are disposed relatively near the rotational axes of the discs being greater than the inward inclination of those which are disposed relatively outward therefrom.

References Cited by the Examiner UNITED STATES PATENTS 2,096,274 10/1937 Beach 241--284 X 2,502,022 3/1950 Paul 241-163 ANDREW R. JUHASZ, Primary Examiner. 

1. A DISINTEGRATING MACHINE COMPRISING A SUPPORT, FIRST AND SECOND DISCS HAVING OPPOSED WORKING FACES WITH A PLURALITY OF INTERDIGITATING RADIALLY SPACED ANNULAR FLANGES THEREON, FIRST MEANS MOUNTING THE FIRST DISC ON SAID BASE FOR ROTATION ABOUT AN AXIS, SECOND MEANS INCLUDING A TRACKWAY PARALLEL TO SAID AXIS AND A CHASSIS ENGAGING SAID TRACKWAY MOUNTING SAID SECOND DISC ON SAID SUPPORT FOR ROTATION ABOUT A HORIZONTAL AXIS ALIGNED WITH THE AFORESAID AXIS, SAID CHASSIS BEING MOVABLE ON SAID TRACKWAY TO PROVIDE VARIABLE AXIAL SPACING BETWEEN THE DISCS, AT LEAST SOME OF SAID ANNULAR FLANGES WHICH ARE ADJACENT TO ONE ANOTHER BEING INCLINED INWARDLY TOWARDS THE AXES OF SAID DISCS WHEREBY ADJUSTMENT OF THE AXIAL SPACING BETWEEN THE DISCS PROVIDES ADJUSTMENT OF THE RADIAL SPACING BETWEEN THE ADJACENT INCLINED ANNULAR FLANGES, A CASING SURROUNDING SAID DISCS, MEANS FOR ROTATING SAID DISCS IN OPPOSITE DIRECTIONS, MEANS FOR FEEDING MATERIAL TO BE DISINTEGRATED CENTRALLY BETWEEN SAID DISCS, AND OUTLET MEANS IN THE PERIPHERY OF SAID CASING FOR THE EGRESS OF MATERIAL AFTER THE LATTER HAS PASSED BETWEEN SAID ANNULAR FLANGES. 